Lubricating system



May 19, 1936- B. D. KUNKI.; 2,041,191

` LUBRICATI'NG SYSTEM l Filed July l5, 1932 2 Sheets-Sheetl B. D. KUNKLE LUBRICAT ING SYSTEM May 19, 1936.

Filed July l5, 1952 2` sheets-sheet 2 Patented May 19, 1936 UNITED STATES PATENT oFFies LUBRICATING SYSTEM Ware Application July 13, 1932, Serial No. 622,179

1 Claim.

This invention relates to a lubricating system, and more particularly to a system that circulates the lubricant so as to lubricate rotating meshing gears and a bearing for a shaft.

It is among the objects of this invention to provide a lubricating system that permits and causes the continuous circulation and supply of lubricant to the bearing or frictional surfaces when in operation. l Another object of this invention is to provide a lubricating system which operates to circulate lubricant when the device with which it is used is in operation.

Another object of this invention is to provide a means for preventing the lubricant from leaking or being carried away along a lubricated shaft either when the machine is idle or in operation.

Another object of this invention is to provide a lubricating system, which while efficient and economical in operation, may also be quickly and easily assembled.

Further objects and advantages of the present invention will be apparent from the following description, reference being had to the accompanying drawings wherein a preferred embodiment of one form of the present invention is clearly shown.

In the drawings:

Fig. 1 is a sectional View of a structure embodying the present invention.

Fig. 2 discloses an enlarged fragmentary sectional view of a portion of the structure disclosed in Fig. 1.

Fig. 3 is a sectional fragmentary View showing a modication of the system.

Fig. 4 is a sectional fragmentary view showing another modication of the lubricating system.

With particular reference to Fig. 1, a housing I0 is formed so as to provide a reservoir or lubricant supply chamber I2. A bearing positioning member I4 is formed integrally with, and adjacent to a side wall I6 of the reservoir I2. A gear I8 is keyed as at 24 to a shaft 20. The level of the lubricant in the reservoir substantially reaches a normal and preferably maximum position indicated by a dot-and-dash line 2B, so that' gear I8 constantly dips into the supply of lubricant.

A motor or prime mover 28 is mounted on and supported by a wall 30 of the housing Ill by Ascrews as 32. A pad 34 of any suitable cushioning material, such as felt, is interposed between the wall I6 of the housing and a side wall 36 of the motor 28. A portion 38 of the housing I0 forms a skirt over the motor 28. End covers 40 and 42 complete the enclosure of the motor 28 partialli7 formed by the side wall 36. An annular sleeve 44 formed on the cover 48 projects through an aperture 46 in the wall 38 and forms a support for a journal bearing 48. The sleeve 44 has a portion 58 press tted into an aperture 4l in the bearing positioning member I4. The bearing 48 provides the bearing for one end of a shaft 52 of the motor 28, while a bearing 54 mounted in th-e cover 42 supports the other end of the shaft 52. The shaft 52 extends through the bearing 48 to an aperture 56 provided by the housing I0.

Since the motor disclosed does not form a part of the present invention, it is believed that the following description of its internal structure will be sufficient in the present application. B8 refers to a centrifugally actuated mechanism for operating a switch 65. That is, when the motor speed rises to a predetermined value, the centrifugal mechanism 68 opens the contacts of the switch to open the circuit to the starting winding of the motor 28. A rotor 'I8 mounted on the shaft 52 is a conventional squirrel cage type of rotor. Stator windings 'I5 are wound on pole structures which are secured to the side walls 38. Fins cause the circulation of air to cool the motor when running. An oiler 9D operatively connected with an oil receiving chamber provides a means for lubricating the bearing 54.

As better disclosed in Fig. 2, a disc 62, having an aperture 64 through which the shaft 52 passes. is secured to the cover 4!) by screws 6B. A gasket 68 interposed between the cover 4l] and the disc 82 prevents leakage of lubricant through the joint thus formed. Lock washers 'I2 are provided for the screws B6. A sleeve member 14 surrounds a portion of the shaft 52, and has a groove 16 near one end which engages the disc 52 to form a joint that will not permit the leakage of lubricant. A chamber 'I8 is formed within the sleeve 44 and adjacent the disc 62 for the accommodation of a lubricant conveying member 82. 'Ihe lubricant conveying member 82 comprises a cylinder having spirally disposed grooves 84 cut on its periphery. As disclosed, the grooves 84 are cut in such a way that when the shaft 52 rotates in a direction as indicated by an arrow 86, the grooves will tend to convey the lubricant in a direction as indicated by an arrow 88. The cylindrical lubricant conveying member 82 has a hollow portion 92 at one end, into which the sleeve 14 projects. A collar 7 94, at one end of the cylindrical member 82, spaces the end of the member 82 from the end wall of the chamber 18.

Also mounted on the shaft 52, and fastened thereto by any suitable means such as a set screw rectly mounted on the shaft 52.

98, is ,a worm gear 96 that meshes with the gear I8. A ball thrust bearing |00 is mounted around the shaft 52 and interposed between the bearing 48 and the worm gear 96. A passage |04 is provided in the sleeve 44 and the bearing 48 to permit lubricant from the gear 96 to lubricate the bearing 48, and pass through the bearing into the chamber 18. A passage |02 in the sleeve 44 provides a communicating opening to permit lubricant to flow from the chamber `|8 back to the reservoir I2.

With particular reference to Fig. 3, parts bearing the same reference numerals as those previously used are similar in structure and perform similar functions, However, in this modification an annular channel member ||0 has a channel wall H2 that surrounds a portion of the shaft 52 and another channel wall ||4 that engages the periphery of an aperture ||6 in the cover 40. The lubricant receiving chamber I8 is thus formed within the sleeve 44 and the annular channel member I I6. The cylindrical lubricant conveying member 82a, in this modification, is disclosed as having a greater number of grooves cut in its pe riphery than the similar member disclosed in Fig. l. A washer of lubricant absorbing material |I8 and a washer |20 surround a portion of the shaft 52 and are interposed between the bearing 48 in the cylindrical member 82a. The side ||2 of the annular channel member I ID projects into the hollow portion 92 of the cylindrical member 82a. A passage |22 in the sleeve 44 permits the lubricant to ow to an auxiliary opening |24 in the sleeve 44 and the bearing 48 to lubricate the latter, and also forms a communicating passage for the flow of lubricant from the chamber I8 to the reservoir I2. A ball |26 is disposed in the passage |22 so as to be free to move in that passage or rest on a seat |28 formed by the sides of the passage.

With particular reference to Fig. 4, reference numerals used in this gure which have been used in previous figures will refer to similar parts which perform similar functions. In this modification, the cylindrical oil conveying member 82h is indi- 'Ihat is, the hollow portion 92 of the member B2b extends a greater distance into the member 82h than in the previous modifications, and an annular member |40 serves as a driving connection between the shaft 52 and the cylindrical member 82h. The annular member |40 is preferably made of a material that it will provide a good frictional engagement between that member and the shaft 52 as well as with the cylindrical member B2b. It is also preferable that the material be one which will permit sliding the cylindrical member B2b longitudinally on the shaft in the assembly so that it may be quickly and easily located at the proper position in the assembly. A washer |42 is mounted on the shaft 52 adjacent the annular member |40. A flanged annular member |44 has a flange |46 which surrounds a portion of the shaft 52 and extends into the hollow portion 92 of the cylindrical member 82h. A gasket |48 is interposd between, and forms a joint with the cover 40 and the member |44 that will not permit the leakage of lubricant therethrough. An annular ring |50 of oil absorbing material is interposed between the ange |46 and the member 82h. A` passage |04 permits the iiow of lubricant to the bearing 48, while the passage |02 is provided for the return of the lubricant to the reservoir I2.

In the operation of the structure disclosed in Figs. 1 and 2, the motor 28 drives the shaft 52 and turns the cylindrical member 82 and the worm gear 9B. The worm gear, in turn, drives the gear I8. The gear I8 picks up lubricant from the supply in the reservoir |2 to lubricate the frictional surfaces 0f the meshing gears |8 and 96. Excess lubricant from the gear 96 lubricates the ball thrust bearing |09 and flows through the passage |04 to the bearing 48, and thence into the chamber '18. Centrifugal force imparted to the lubricant by the cylindrical member 82 tends to force the oil to the passage or space between the cylindrical member 82 and the wall of the chamber i8. Then, assuming the direction of rotation as indicated by the arrow 86 in Fig. 2, the lubricant is conveyed by the spirally disposed grooves 84 in the cylindrical member 82, in a direction corresponding with that of the arrow B8. The lubricant is thus forced through the passage |02 and back to the reservoir |2. Hence, it may be seen that the cylindrical member 82 acts as a lubricant pump, and utilizes centrifugal force in its operation, as well as the conveying action of the spirally disposed lubricant conveying grooves. Since some lubricant will always be in the bottom of the chamber 18, it is necessary to provide a means for preventing that lubricant from leaking out of the chamber 'I8 along the shaft and into the motor. The annular sleeve member 'I4 forms a seal with the disc 62 and extends along the shaft to a heighth greater than that reached by the level of the lubricant in the chamber under normal operating conditions. When the machine is stopped, some of the lubricant which was in the process of circulation will ow into the chamber 18. Hence, to prevent that lubricant from leaking into the motor along the shaft, the sleeve member I4 extends beyond the level reached by the lubricant in the chamber 18.

In the operation of the modification disclosed in Fig. 3, lubricant flows into the passage |22, and since the ball |26 seals the passage the lubricant will rise to a suhcient heighth to pass through the passage i 24 to lubricate the bearings. The annular ring I i8 of lubricant absorbing material tends to reduce the rapidity of flow of the lubricant from the bearing. When sufficient lubricant accumulates in the chamber 18, the cylindrical member 82a tends to force the lubricant out of the chamber into the passage |22. When the force cf the lubricant reaches the value suflcient to open the valve formed by the ball |26, the lubricant may ow out through the passage |22. Since this structure is adapted for slower circulation in the lubricant than the system disclosed in Figs. l and 2, a greater number of grooves have been cut on the surface of the cylindrical member 82 and the pitch of the groove is consequently reduced. The rate at which the cylindrical member 82a, may convey the lubricant is proportional to the pitch of the groove and the speed of rotation. The flange |2 extends beyond the normal level of the lubricant in the chamber 78 when the shaft is either rotating or stationary. The joint between the member l0 and the cover 40 forms a seal through which lubricant cannot pass.

In the operation of the device as disclosed in Fig. 4, the cylindrical member B2b is driven by the shaft through the engagement of each with the member |40. driven directly by the shaft as in the previously explained modification, and the driving relation is brought about by having a shrink fit between the shaft and cylindrical member, the cylindrical member must be quite accurately placed at the If the cylindrical member is n time it is mounted on the shaft ln order to t properly into the assembly. By using any suitable material such as cork for a member |40, sufficient frictional engagement may be had between that material and the shaft to drive the cylindrical member and pump the lubricant, and yet the cylindrical member may be moved along the shaft slightly in the assembly of the complete system in order to locate it in its proper position. The washer |42 and the lubricant absorbing material |50 prevent lubricant from working between the frictionally engaged surfaces of the shaft and the member |40. The joint between the member |44, the gasket |48 and the cover |40 provides a seal between those members through which lubricant cannot pass.

While the form Vof embodiment of the present invention as herein disclosed, constitutes a preferred form, it is to be understood that other forms might be adopted, all coming within the scope of the claim which follows.

What is claimed is as follows:

A lubricating system comprising, in combination, a lubricant supply chamber having a supply of lubricant therein; a bearing support adjacent to the lubricant supply chamber, and having a bearing supported thereby, said bearing support and bearing providing cooperating lubricant conducting passages therein and an auxiliary charnber; a shaft rotatably mounted in said bearing and extending into the auxiliary chamber; one of said passages providing communication between said chambers, and the other of said passages providing communication to said bearing; valve means in said one passage restricting the flow therethrough in one direction; and lubricant pumping means within the `auxiliary chamber and driven by the shaft for forcing lubricant through one of said passages from the auxiliary chamber to the supply chamber.

BAYARD D. KUNKLE. 

